Apparatus for sensing cam phaser position

ABSTRACT

A first target wheel has an opening and rotates about an axis of rotation to move the opening along a generally circular path. A second target wheel adjacent the first target wheel has a second projection projecting into the opening of the first target wheel with the second projection being movable along the generally circular path. A single sensor is positioned adjacent the generally circular path and senses movement of the opening and the second projection past the sensor. An electronic controller may be used to process signals from the sensor to determine the relative angular difference between the first target wheel and the second target wheel.

TECHNICAL FIELD

This disclosure relates generally to internal combustion engines havingvariable valve timing capability and, more particularly, to an apparatusfor sensing the cam phaser position of the engine.

BACKGROUND

Valve timing within internal combustion engines may be varied to alterperformance characteristics and increase efficiency of operation. Somesystems use a cam phaser with a first element driven in a fixedrelationship to the crankshaft and a second element mounted to the endof the camshaft and adjacent to the first element. In one example, thefirst element is a stator mounted inside a crankshaft-driven componentand having a plurality of radially-disposed inwardly-extendingspaced-apart lobes and an axial bore. The second element is a vanedrotor mounted to the end of the camshaft through the stator axial boreand having vanes disposed between the stator lobes to form actuationchambers therebetween such that limited relative rotational motion ispossible between the stator and the rotor.

Relative movement between the components of the cam phaser controls thepositioning of the camshaft and the valves relative to the crankshaftand the pistons of the engine. In order to efficiently use such asystem, the position of the camshaft relative to the crankshaft must bemonitored on an ongoing or continuous basis. This sensing of relativeposition, or cam phase angle sensing, is often determined by monitoringa cam target wheel associated with the second element of the cam phaserto determine the position of the camshaft, monitoring the position ofthe crankshaft, and comparing their positions to determine the relativeangular difference between the camshaft and the crankshaft.

In large engines, tolerance stack-up and torsional issues may impact theaccuracy of the relationship between the valves and pistons obtained bymonitoring the positions of the camshaft and the crankshaft.Accordingly, it is desirable to increase the accuracy of the cam phaseangle sensing without increasing complexity and cost.

The foregoing background discussion is intended solely to aid thereader. It is not intended to limit the innovations described herein norto limit or expand the prior art discussed. Thus the foregoingdiscussion should not be taken to indicate that any particular elementof a prior system is unsuitable for use with the innovations describedherein, nor is it intended to indicate any element, including solvingthe motivating problem, to be essential in implementing the innovationsdescribed herein. The implementations and application of the innovationsdescribed herein are defined by the appended claims.

SUMMARY

In one aspect, a system for sensing the relative angular differencebetween first and second rotating members that rotate relative to eachother is provided. The system uses adjacent target wheels associatedwith the rotating members. A first target wheel has an opening androtates about an axis of rotation to move the opening along a generallycircular path within a plane generally perpendicular to the axis ofrotation. A second target wheel adjacent the first target wheel alsorotates about the axis of rotation. The second target wheel has a secondprojection projecting into the opening of the first target wheel withthe second projection being rotatable along the generally circular pathand about the axis of rotation. A sensor, positioned adjacent thegenerally circular path, is disposed to sense movement of the openingand the second projection past the sensor. An electronic controller maybe used to process signals from the sensor to determine the relativeangular difference between the first target wheel and the second targetwheel. When used with an internal combustion engine, the system mayinclude a hydraulic system having a cam phaser to change the relativeposition of the first target wheel and the second target wheel. In thisway, the relative angular difference between a camshaft and a crankshaftmay be changed control the operating characteristics of the engine.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a diagrammatic view of an engine and control in accordancewith the disclosure;

FIG. 2 is a partial cross section of a combustion cylinder of an enginein accordance with the disclosure;

FIG. 3 is an exploded perspective view of a cam phaser sub-assemblytogether with intake and exhaust camshafts and a cylinder head;

FIG. 4 is a perspective view of a camshaft and cam phaser in accordancewith the disclosure;

FIG. 5 is an end view of cam phaser with the cover plate removed;

FIG. 6 is a diagrammatic end view of the interaction between a pair oftarget wheels;

FIG. 7 is a diagrammatic end view of the first target wheel;

FIG. 8 is a diagrammatic end view of the second target wheel;

FIG. 9 is an enlarged diagrammatic top view of the interaction between apair of target wheels; and

FIG. 10 is a diagrammatic end view of the interaction between a pair oftarget wheels of an alternate embodiment.

DETAILED DESCRIPTION

Referring to FIGS. 1-2, internal combustion engine 100 includes acrankcase 102 having a plurality of cylinders 202 with a reciprocatingpiston 203 mounted in each cylinder. A rotatable crankshaft 106 iscoupled to each piston 203 via connecting rod 204 (partially shown). Anintake camshaft 108 and an exhaust camshaft 110 are driven by thecrankshaft 106 via a timing belt or chain 112 that engages a sprocket114 on each camshaft. Each cylinder 202 is operably associated with aninjector, an intake runner 206, and an exhaust runner 208.

During operation of the internal combustion engine 100, air enters eachcylinder 202 via its respective intake runner 206. While in the cylinder202, the air mixes with fuel injected from the injector to form acombustible mixture. In an alternative embodiment, the fuel is mixedwith intake air before it enters the engine cylinders to yield acombustible mixture. In either engine configuration, the combustiblemixture is compressed via piston 203 and is ignited by a spark producingdevice. Although the disclosed embodiment describes a spark ignitionengine operating on gaseous hydrocarbon fuel such as natural gas,compression ignition engines or engines operating on gasoline or anyother hydrocarbon fuel are contemplated and are suited for the devicesdisclosed herein. Exhaust gas remaining in the cylinder 202 afterignition is evacuated via the exhaust runner 208 and the process isrepeated.

Cylinder 202 includes reciprocating piston 203 therewithin connected tothe rotatable crankshaft 106 via connecting rod 204 (partially shown). Acylinder head 210 forms portions of the intake runner 206 and theexhaust runner 208. A reciprocating intake valve 212 is mounted in thecylinder head 210 and disposed to selectively block air entering thecylinder 202 from the intake runner 206. Similarly, a reciprocatingexhaust valve 214 is mounted in cylinder head 210 and selectively blocksexhaust gas present in the cylinder 202 after a power stroke of theengine from entering the exhaust runner 208. Although single intake andexhaust valves are shown for simplicity, the internal combustion engine100 may include multiple valves per cylinder.

As depicted, the opening and closing of the intake valves 212 andexhaust valves 214 in the illustrated embodiment is accomplished by twooverhead camshafts, but other configurations may be used. Moreover,although dedicated intake and exhaust camshafts are shown, alternateengine configurations may include a single camshaft operating both theintake and exhaust valves of the engine. In the illustrated embodiment,the intake camshaft 108 includes a plurality of intake lobes 216 thatform eccentric features configured to push the intake valve 212 openthrough a corresponding intake valve bridge 218 as the intake camshaft108 rotates. Similarly, the exhaust camshaft 110 includes exhaust lobes220 that push the exhaust valve 214 open through a corresponding exhaustvalve bridge 222. Other structures for operating valves of cylindersarranged in any inline, V-shaped, or any other configuration are alsocontemplated.

In the depicted embodiment, a cam phaser 116 is coupled to both theintake camshaft 108 and exhaust camshaft 110 and each may behydraulically controlled to create a variable rotational offset betweenthe respective camshafts 108, 110 and the crankshaft 106. The degree ofrotational offset generated by each cam phaser 116 enables the internalcombustion engine 100 to be tuned for specific performancecharacteristics by varying the overlap between the intake valves 212 andthe exhaust valves 214, as desired. More specifically, performancecharacteristics of the internal combustion engine may be altered and theefficiency of operation increased by controlling the valve overlapthrough the cam phasers 116.

Referring to FIGS. 3-5, a cam phaser sub-assembly 302 is depicted withone cam phaser 116 and one control valve sub-assembly 304 associatedwith each camshaft. Each cam phaser 116 includes one sprocket 114 forengaging and being driven by the engine timing belt or chain 112. Eachcamshaft 108, 110 extends through sprocket 114 and is configured torotate independently of the sprocket. A generally cylindrical lobedstator 502 is fixed to sprocket 114 by a plurality of fasteners and hasa plurality of radial chambers or lobes 504. A vaned rotor 506 ispositioned within lobed stator 502 and has a central bore 508 and aplurality of vanes 510. The number of vanes 510 of vaned rotor 506corresponds to the number of lobes 504 of lobed stator 502. Vaned rotor506 is provided with fluid passageways 512 for delivering pressurizedfluid such as oil to opposite sides of each vane 510 in each lobe 504 inorder to adjust the angular position of the vaned rotor 506 relative tothe lobed stator 502. A cover plate 305 is sealingly and concentricallydisposed against the lobed stator 502 to seal the lobes 504 and vanedrotor 506. The cam phaser 116 is secured to the end of each camshaft bya bolt 307 which also fixes the vaned rotor 506 of the cam phaser 116 tothe camshaft without engaging the lobed stator 502. As such, eachcamshaft 108, 110 and vaned rotor 506 may rotate relative to the lobedstator 502 and sprocket 114 by an amount equal to the spacing orclearance 514 between the vanes of the vaned rotor and the lobes of thelobed stator.

Referring to FIGS. 6-9, a generally planar first target wheel 306 has aplurality of first projections such as first teeth 602 extendingradially about the axis of rotation 118 of the camshaft 108, 110 and ismounted so as to be fixed to the lobed stator 502. As depicted, firsttarget wheel 306 is rotationally symmetrical and includes four quadrants604 with four identical arrays of five equally spaced first teeth 602with a position designating space or opening 606 within each array. Inother words, first target wheel 306 has twenty first teeth 602 spacedabout the outer perimeter as if the first target wheel were formed withtwenty-four first teeth fifteen degrees apart and every sixth tooth hasbeen removed to create the opening. Each opening 606 has a forward edge608 and a trailing edge 609 for triggering wheel speed sensor 120. Asdepicted, the width of each opening 606 is approximately equal to thewidth of three first teeth 602. It is contemplated that the opening 606may have a different width so long as sufficient clearance area 607 isprovided within opening 606 to permit movement of a second tooth 612therein. Rotation of first target wheel 306 about the axis of rotation118 of camshaft 108, 110 causes first teeth 602 and thus openings 606 torotate or move along a generally circular path within the plane of thefirst target wheel 306 and generally perpendicular to the axis ofrotation.

A generally planar second target wheel 308 has a plurality of positiondesignating tabs or second projections such as second teeth 612extending or projecting in a direction generally parallel to the axis ofrotation 118 of the camshaft 108, 110. Second target wheel 308 ismounted so as to be fixed to the camshaft 108, 110 and vaned rotor 506.As depicted, second target wheel 308 is rotationally symmetrical andincludes four quadrants with one second tooth 612 in each quadrant. Eachsecond tooth 612 has a forward edge 618 and a trailing edge 619 fortriggering wheel speed sensor 120. The second teeth 612 are equallyspaced apart on second target wheel 308 and, as such, are ninety degreesapart. Rotation of second target wheel 308 about the axis of rotation118 of camshaft 108, 110 causes second teeth 612 to rotate or move alonga generally circular path generally perpendicular to the axis ofrotation.

The first target wheel 306 and the second target wheel 308 arepositioned adjacent each other along the axis of rotation 118 of thecamshaft 108, 110 with a clearance or gap 622 therebetween. Each secondtooth 612 extends into the plane of the first target wheel 306 and isaligned with and projects into one of the openings 606 thereof in orderto create pairs of openings and second teeth. The first target wheel 306is fixed to the lobed stator 502 so that the first target wheel rotateswith the lobed stator. The second target wheel 308 is fixed to the vanedrotor 506 and the camshaft 108, 110 so that the second target wheelrotates with the vaned rotor and the camshaft. In an alternateembodiment, cam phaser sub-assembly 302 may be configured so that firsttarget wheel 306 is fixed to the vaned rotor 506 and the camshaft 108,110 and the second target wheel 308 is fixed to the lobed stator 502.Rotation of the camshaft 108, 110 and the cam phaser 116 will cause theopenings 606 and the second teeth 612 to rotate or move along agenerally circular path about the axis of rotation 118 of the camshaft108, 110. Rotation of the sprocket 114 while the vaned rotor 506 isfixed relative to the lobed stator 502 will cause rotation of theopenings 606 and the second teeth 612 about the axis of rotation butwithout relative motion therebetween. Rotation of the vaned rotor 506relative to the lobed stator 502 will cause rotational motion of theopenings 606 relative to the second teeth 612. Clearance areas 607 aredimensioned to permit rotational movement of second teeth 612 withinopenings 606 without impeding the rotation of vaned rotor 506 relativeto lobed stator 502.

As best seen in FIG. 9, each second tooth projects into one of theopenings 606 of the first target wheel 306. Although depicted asextending into the opening 606 to a position approximately eightypercent of the distance across the first teeth 602 and openings 606(i.e., in the direction of the thickness of the first target wheel 306),the second teeth 612 may extend a longer or shorter distance orthickness “t” provided that they extend a sufficient distance so wheelspeed sensor 120 is able to sense or detect the passage of each secondtooth. For example, the second teeth 612 could extend to or past the faredge 610 of the first target wheel 306 provided that such configurationdoes not create an obstacle to relative rotation between the lobedstator 502 and the vaned rotor 506 as well as any other components ofthe cam phaser 116. In another example, the first teeth have a thickness“t” and it is believed that configuring the second teeth to extend atleast to the midpoint or fifty percent of the distance across thethickness will provide a sufficient surface or edge to be detected bywheel speed sensor 120.

Other configurations of pairs of openings and second teeth that movewithin a common generally circular path could be utilized. For example,FIG. 10 depicts an alternate embodiment of a pair of target wheels suchas generally planar third target wheel 1002 and generally planar fourthtarget wheel 1004. Such configuration permits the wheel speed sensor 120to be positioned generally perpendicular to the plane of the targetwheels as shown in phantom (FIG. 10) rather than along an edge of thetarget wheels (FIGS. 3, 9). Third target wheel 1002 is rotationallysymmetrical and includes four equally spaced position designatingtriangular openings 1006 therein. Each triangular opening 1006 has aleading edge 1008 and a trailing edge 1009 for triggering wheel speedsensor 120. The width of triangular opening 1006 is sufficient toprovide sufficient clearance area 1007 within the opening to permitrotational movement of triangular projection 1012 therein. Rotation ofthird target wheel 1004 about the axis of rotation 118 of camshaft 108,110 causes triangular openings 1006 to rotate or move along a generallycircular path within a plane generally perpendicular to the axis ofrotation.

Fourth target wheel 1004 is rotationally symmetrical and includes fourequally spaced position designating triangular projections 1012extending or projecting from a surface thereof in a direction generallyparallel to the axis of rotation 118 of the camshaft 108, 110. Eachtriangular projection 1012 has a leading edge 1018 and a trailing edge1019 for triggering wheel speed sensor 120.

The third target wheel 1002 and the fourth target wheel 1004 areconfigured to be positioned adjacent each other along the axis ofrotation 118 of the camshaft 108, 110 in a manner substantially similarto the manner in which first target wheel 306 and second target wheel308 are mounted. Each triangular projection 1012 of fourth target wheel1004 extends into the plane of the third target wheel 1002 and isaligned with and projects into one of the triangular openings 1006thereof in order to create pairs of third and fourth triangular openingsand projections. Rotation of the camshaft 108, 110 and the cam phaser116 will cause the triangular openings 1006 and the triangularprojections 1012 to rotate or move along a generally circular path aboutthe axis of rotation 118 of the camshaft 108, 110. Rotation of thesprocket 114 while the vaned rotor 506 is fixed relative to the lobedstator 502 will cause rotation of the triangular openings 1006 and thetriangular projections 1012 about the axis of rotation but withoutrelative motion therebetween. Rotation of the vaned rotor 506 relativeto the lobed stator 502 will cause rotational motion of the triangularopenings 1006 relative to the triangular projections 1012. Clearanceareas 1007 are dimensioned to permit rotational movement of thetriangular projections 1012 within triangular openings 1006 withoutimpeding the rotation of vaned rotor 506 relative to lobed stator 502.

Although referred to as target wheels, the first target wheel 306 andthe second target wheel 308 could be structures of various shapesprovided that they include openings and projections that rotate aboutthe axis of rotation 118 to define a generally circular path. Forexample, the openings and projections could be formed as components ofthe housing of the lobed stator 502 or the cover plate 305 or othercomponents of the cam phaser 116. First target wheel 306 and secondtarget wheel 308 are depicted with four pairs of openings and secondteeth. Other numbers of pairs may be used with a greater numbergenerally increasing the accuracy of the measurement and a lesser numbergenerally decreasing the accuracy of the measurement.

The wheel speed sensor 120 may be any type of sensing device includingHall effect sensors, variable reluctance sensors and other devices thatwill perform a similar function. The wheel speed sensor 120 detects theforward edges 608 and the trailing edges 609 of the openings 606 on thefirst target wheel 306 and the forward edges 618 and the trailing edges619 of the second teeth 612 on the second target wheel 308 and providesa series of signal pulses to an electronic controller 122. Based uponthe signal pulses, the electronic controller 122 determines the phaseangle between the camshaft 108, 110 and the crankshaft 106. Theelectronic controller 122 may be any type of controller such as a singlemicroprocessor or a plurality of microprocessors and could also includeadditional microchips and components for random access memory, storage,and other functions as necessary to enable the functionalities describedherein.

Control valve sub-assembly 304 includes a spool valve (not shown)operative to control the passage of pressurized fluid from the hydraulicsystem 124 within the cam phaser 116. Varying the axial position of thespool valve varies the amount of pressurized fluid delivered to oppositesides of vanes 510 of vaned rotor 506 and the rotational position of thevanes 510 in the lobes 504 of lobed stator 502 and, thus, the phaserelationship between the sprocket 114 and the camshaft 108, 110.Electronic controller 122 may provide signals for controlling thehydraulic system 124 and control valve sub-assembly 304.

In operation, the crankshaft 106 rotates and drives the sprockets 114associated with each camshaft via timing belt or chain 112. The rotationof sprockets 114 causes the cam phasers 116 to rotate. As the camphasers 116 rotate, the openings 606 on the first target wheel 306 andthe second teeth 612 on the second target wheel 308 rotate together andpass wheel speed sensor 120. Movement of each forward edge and trailingedge past the sensor creates a series of signals that are received byelectronic controller 122. Electronic controller 122 determines therelative angular difference between the first target wheel 306 and thesecond target wheel 308 based upon the timing of the signals receivedfrom the wheel speed sensor 120. The electronic controller 122 thenutilizes the relative angular difference between the target wheels todetermine the relative angular difference between the crankshaft 106 andeach camshaft 108, 110. Depending on the desired operating conditions,electronic controller may send a signal to an actuation system such ashydraulic system 124 to change the relative angular difference the lobedstator 502 and the vaned rotor 506 in order to change the operatingcharacteristics of internal combustion engine 100. If the relativeangular difference between the lobed stator 502 and the vaned rotor 506is changed, the relative angular difference between the openings 606 ofthe first target wheel 306 and the second teeth 612 of the second targetwheel 308 will change and such change will be monitored and confirmed bythe electronic controller

The configuration of first and second rotating members in which thefirst rotating member has an opening and the second rotating member hasa projection located within the opening provides a space efficientmanner of sensing the relative angular difference between first andsecond rotating members. In addition, the structure provides the furtheradvantage of permitting a sensor to be located in alternate orientationsby changing the orientation and location of the opening and projectionassociated with the first and second rotating members.

INDUSTRIAL APPLICABILITY

The industrial applicability of the system described herein will bereadily appreciated from the foregoing discussion. The presentdisclosure is applicable to many types of systems having adjacentmembers that rotate relative to each other. One such system is aninternal combustion engines having variable valve phasing. Such internalcombustion engines may adjust valve phasing during engine operationbased on various operating parameters such as engine speed, engine load,altitude, fuel quality, and others factors. It may be desirable tochange the valve phasing based upon changes in engine speed and load,changes in altitude, as well as changes in fuel quality in order tochange the operating characteristics of an engine such as to dynamicallyincrease the performance or the efficiency of the engine.

During the course of operating an engine, it is necessary to monitor therelative angular difference between the camshaft and the crankshaft. Inlarge engines, tolerance stack-up and torsional issues may impact theaccuracy of the relationship between the valves and pistons obtained bymonitoring the relative angular difference between the camshaft and thecrankshaft. Torsional affects within the system including thecrankshaft, gear train, and camshaft may cause inconsistency in themeasurement and monitoring of the relationship between the camshaft andthe crankshaft. Moving the measurement points close together reduces theimpact of the torsional noise and inconsistency in order to provide moreconsistent measurement of the relative angular difference between thecrankshaft and camshaft.

While operating the engine, a system having a pair of adjacent targetwheels may be used to monitor the relative angular difference betweenthe crankshaft and camshaft. A first target wheel has an opening androtates about an axis of rotation to move the opening along a generallycircular path within a plane generally perpendicular to the axis ofrotation. A second target wheel adjacent the first target wheel alsorotates about the axis of rotation. The second target wheel has a secondprojection projecting into the opening of the first target wheel withthe second projection being movable along the generally circular pathand about the axis of rotation. A single sensor is positioned adjacentthe generally circular path and senses movement of the opening and thesecond projection past the sensor. An electronic controller may be usedto process signals from the sensor to determine relative angulardifference between the first target wheel and the second target wheel.

In addition, the system may include a hydraulic system having a camphaser to change the relative angular difference between the firsttarget wheel and the second target wheel and thus also change therelative angular difference between the camshaft and the crankshaft inorder to change the operating characteristics of an engine.

It will be appreciated that the foregoing description provides examplesof the disclosed system and technique. However, it is contemplated thatother implementations of the disclosure may differ in detail from theforegoing examples. All references to the references to the disclosureor examples thereof are intended to reference the particular examplebeing discussed at that point and are not intended to imply anylimitation as to the scope of the disclosure more generally. Alllanguage of distinction and disparagement with respect to certainfeatures is intended to indicate a lack of preference for thosefeatures, but not to exclude such from the scope of the disclosureentirely unless otherwise indicated.

Recitation of ranges of values herein are merely intended to serve as ashorthand method of referring individually to each separate valuefalling within the range, unless otherwise indicated herein, and eachseparate value is incorporated into the specification as if it wereindividually recited herein. All methods described herein can beperformed in any suitable order unless otherwise indicated herein orotherwise clearly contradicted by context.

Accordingly, this disclosure includes all modifications and equivalentsof the subject matter recited in the claims appended hereto as permittedby applicable law. Moreover, any combination of the above-describedelements in all possible variations thereof is encompassed by thedisclosure unless otherwise indicated herein or otherwise clearlycontradicted by context.

The invention claimed is:
 1. A system for sensing a relative angulardifference between first and second rotating members, the systemcomprising: a first target wheel having an opening, the first targetwheel being rotatable about an axis of rotation to move the openingalong a generally circular path within a plane generally perpendicularto the axis of rotation; a second target wheel adjacent the first targetwheel and being rotatable about the axis of rotation, the second targetwheel having a second projection, the second projection projecting intothe opening, the second projection being rotatable along the generallycircular path and about the axis of rotation; a sensor adjacent thegenerally circular path for sensing movement of the opening and thesecond projection past the sensor; and a cam phaser having a lobedstator and a vaned rotor, the first target wheel being secured to one ofthe lobed stator and the vaned rotor, the second target wheel beingsecured to another of the lobed stator and the vaned rotor.
 2. Thesystem of claim 1, wherein the first target wheel is secured to thelobed stator and the second target wheel is secured to the vaned rotor.3. The system of claim 1, wherein the first target wheel and the secondtarget wheel are rotationally symmetrical about the axis of rotation. 4.The system of claim 1, further including an electronic controllerconfigured to process signals from the sensor and determine the relativeangular difference between the first target wheel and the second targetwheel.
 5. The system of claim 4, wherein the electronic controllerutilizes the relative angular difference between the first target wheeland the second target wheel to control signals to an actuation systemoperative to control the relative angular difference between the firsttarget wheel and second target wheel.
 6. The system of claim 5, whereinthe actuation system is a hydraulic system.
 7. The system of claim 1,further including a clearance area within the opening to permit movementof the second projection therein and relative rotation of the firsttarget wheel and the second target wheel.
 8. The system of claim 1,further including a plurality of spaced apart first teeth within theplane of the generally circular path, and a plurality of spaced apartsecond teeth, the second teeth extending into the plane of the generallycircular path.
 9. The system of claim 8, wherein the second teeth areevenly spaced around the second target wheel about the axis of rotation.10. An internal combustion engine, comprising: at least one cylinderhaving a reciprocating piston therein; at least one valve associatedwith the at least one cylinder and operable by a camshaft, the camshaftrotating about an axis of rotation, the at least one valve beingconfigured to open and close over a predetermined range of crankshaftrotation, a cam phaser operatively associated with the camshaft andincluding a lobed stator and a vaned rotor, a first target wheel beingsecured to one of the lobed stator and the vaned rotor, the first targetwheel having an opening, the first target wheel being rotatable aboutthe axis of rotation to rotate the opening along a generally circularpath within a plane generally perpendicular to the axis of rotation, asecond target wheel adjacent the first target wheel, the second targetwheel being rotatable about the axis of rotation and secured to anotherof the lobed stator and the vaned rotor, the second target wheel havinga second projection projecting into the opening of the first targetwheel, the second projection being rotatable along the generallycircular path and about the axis of rotation; a sensor adjacent thegenerally circular path for sensing movement of the opening and thesecond projection past the sensor; and an electronic controllerconfigured to process signals from the sensor and determine a relativeangular difference between the first target wheel and the second targetwheel.
 11. The internal combustion engine of claim 10, wherein the firsttarget wheel is secured to the lobed stator and the second target wheelis secured to the vaned rotor.
 12. The internal combustion engine ofclaim 10, wherein the electronic controller utilizes the relativeangular difference between the first target wheel and the second targetwheel to control signals to an actuation system operative to control therelative angular difference between the first target wheel and thesecond target wheel.
 13. The internal combustion engine of claim 10,further including a clearance area within the opening to permit movementof the second projection therein and relative rotation of the firsttarget wheel and the second target wheel.
 14. The internal combustionengine of claim 10, wherein the first target wheel has a plurality ofspaced apart first teeth within the plane of the generally circular pathand defines a plurality of openings, the second target wheel has aplurality of spaced apart second teeth, and each second tooth extendsinto one of the openings and the plane of the generally circular path.15. The internal combustion engine of claim 14, wherein the first teethhave a first thickness generally perpendicular to the generally circularpath and the second teeth extend at least past a midpoint of thethickness of the first teeth.
 16. The internal combustion engine ofclaim 14, wherein the second teeth are evenly spaced about the secondtarget wheel around the axis of rotation.
 17. The internal combustionengine of claim 10, wherein the first target wheel and the second targetwheel are rotationally symmetrical about the axis of rotation.
 18. A camphaser sub-assembly for operatively coupling with a camshaft,comprising: a lobed stator configured to be driven by a crankshaft; avaned rotor fixed to the camshaft, the vaned rotor being positionedwithin and configured to rotate relative to the lobed stator; a firsttarget wheel secured to one of the lobed stator and the vaned rotor, thefirst target wheel having a plurality of spaced apart openings and beingrotatable about an axis of rotation of the camshaft to move the openingsalong a generally circular path within a plane generally perpendicularto the axis of rotation; and a second target wheel adjacent the firsttarget wheel and secured to another of the lobed stator and the vanedrotor, the second target wheel having a plurality of spaced apart secondprojections and being rotatable about the axis of rotation, each secondprojection projecting into one of the openings, the second projectionsbeing rotatable along the generally circular path and about the axis ofrotation.